EP2416000B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP2416000B1
EP2416000B1 EP10761560.1A EP10761560A EP2416000B1 EP 2416000 B1 EP2416000 B1 EP 2416000B1 EP 10761560 A EP10761560 A EP 10761560A EP 2416000 B1 EP2416000 B1 EP 2416000B1
Authority
EP
European Patent Office
Prior art keywords
fuel
fuel discharge
nozzle
valve
valve seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10761560.1A
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German (de)
English (en)
French (fr)
Other versions
EP2416000A1 (en
EP2416000A4 (en
Inventor
Akira Akabane
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Keihin Corp
Original Assignee
Keihin Corp
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Filing date
Publication date
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Publication of EP2416000A1 publication Critical patent/EP2416000A1/en
Publication of EP2416000A4 publication Critical patent/EP2416000A4/en
Application granted granted Critical
Publication of EP2416000B1 publication Critical patent/EP2416000B1/en
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • F02M51/0682—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto the body being hollow and its interior communicating with the fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
    • F02M61/145—Arrangements of injectors with respect to engines; Mounting of injectors the injection nozzle opening into the air intake conduit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/1813—Discharge orifices having different orientations with respect to valve member direction of movement, e.g. orientations being such that fuel jets emerging from discharge orifices collide with each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
    • F02M35/10216—Fuel injectors; Fuel pipes or rails; Fuel pumps or pressure regulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/044—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit downstream of an air throttle valve

Definitions

  • the present invention relates to a fuel injection valve that is mainly used in a fuel supply system of an internal combustion engine and, in particular, to an improvement of a fuel injection valve that includes a valve body, a valve seat member having an annular conical valve seat on which the valve body is seated in an openable and closable manner, and a nozzle that is provided so as to be connected to a front end part of the valve seat member so as to be positioned on the downstream side of the valve seat and has a plurality of fuel discharge holes arranged around the axis of the valve seat member, an inner end face of the nozzle, on which inlets of the plurality of fuel discharge holes open, being a concave conical face or spherical face having a diameter that decreases in going toward the front of the nozzle.
  • Such a fuel injection valve is already known, as disclosed by Japanese Patent Application Laid-open No. 2006-207419 below.
  • a fuel injection valve of the generic kind is also known from DE 100 32 336 A1 and EP 1 555 430 A1 .
  • the present invention has been accomplished in light of such circumstances, and it is an object thereof to provide a fuel injection valve that reduces the loss of fuel injection energy and makes the outline of a fuel spray form produced by injected fuel clear, thus improving penetration properties and, moreover, improving atomization in an extremity part of the fuel spray form close to an engine intake valve, thereby contributing to an improvement of engine combustion efficiency and, consequently, to an improvement of output and fuel consumption performance.
  • a preferred embodiment of the present invention provides a fuel injection valve in which, in a state in which the fuel injection valve is mounted on an intake manifold of an internal combustion engine, two independent fuel spray-form beams produced from injected fuel are supplied toward first and second ports, the fuel injection valve comprising a valve body, a valve seat member having an annular conical valve seat on which the valve body is seated in an openable and closable manner, and a nozzle that has a plurality of fuel discharge holes and is provided in a front end part of the valve seat member so as to be positioned on the downstream side of the valve seat, an inner end face of the nozzle, on which inlets of the plurality of fuel discharge holes open, being a conical or spherical face that is concave in going toward the front of the nozzle, characterized in that the plurality of fuel discharge holes are arranged on the same virtual circle having an axis
  • a gap between the fuel discharge holes in each of the fuel discharge hole groups is set smaller than a gap between the two fuel discharge hole groups.
  • valve seat member and the nozzle are formed integrally using the same material.
  • fuel injected from the fuel discharge hole can produce a fuel spray form as a fuel film having an arc-shaped cross section with a convex face facing the nozzle outer periphery side.
  • This fuel spray form has a clear outline and does not cause wasteful scattering; furthermore, in the fuel discharge hole there is no direct collision of fuel flow with its inner face, the loss of injection energy is small, and the penetration properties of the fuel spray form can therefore be improved.
  • each fuel discharge hole group fuel spray forms injected and produced from fuel discharge holes at opposite outside positions are inclined toward the fuel spray form injected and produced from the fuel discharge hole at the middle position, confluence therewith is promoted, a fuel spray-form beam having a clear outline can be produced, and it is thereby possible to enhance further effectively the penetration properties of the first and second fuel spray-form beams.
  • the fuel film having an arc-shaped cross section which produces the fuel spray form, increases in diameter and greatly decreases in film thickness in going toward the engine intake valve, a good atomization state is given due to high speed contact with air, and therefore atomization in an extremity part of the fuel spray form close to the intake valve can be improved.
  • a good atomization state is given due to high speed contact with air, and therefore atomization in an extremity part of the fuel spray form close to the intake valve can be improved.
  • the fuel discharge holes therefore have center lines that are substantially parallel to the axis of the valve seat member, and machining of each fuel discharge hole by means of piercing or a laser can be carried out easily without being affected by surrounding objects, such as a peripheral wall of the valve seat member.
  • each of the first and second fuel discharge hole groups by fuel injected from the plurality of fuel discharge holes, two independent first and second fuel spray-form beams can thus be produced, the outlines of these fuel spray-form beams are also clear, there is no wasteful scattering, and high penetration properties can be obtained.
  • valve seat member due to integration of the valve seat member and the nozzle using the same material, not only can a step of joining to the valve seat member by welding, etc. be omitted and the production step and the structure be made simple, but it is also possible to prevent the valve seat from being distorted by a joining step and improve the precision of the valve seat and, consequently, the valve sealing. Furthermore, it is possible to easily carry out machining of the fuel discharge hole at the correct position with respect to the valve seat, and dimensional control can also be carried out easily.
  • first and second intake ports P1 and P2 are formed in a cylinder head Eh of an engine E so as to correspond to one cylinder Ec, the first and second intake ports P 1 and P2 being bifurcated with a partition wall Eha interposed therebetween, and openings of the first and second intake ports P1 and P2 to the cylinder Ec are opened and closed by a pair of intake valves Ei and Ei.
  • an intake manifold Em Joined to one side of the cylinder head Eh is an intake manifold Em equipped with an intake path communicating in common with the first and second intake ports P1 and P2.
  • a fuel injection valve I of the present invention is mounted in this intake manifold Em, and when it is open two independent fuel spray-form beams F1 and F2 produced by injected fuel are supplied toward the first and second intake ports P1 and P2.
  • the direction in which the first and second intake ports P1 and P2 are arranged on a front end face of the fuel injection valve I is defined as X
  • the direction perpendicular to the arrangement direction X is defined as Y.
  • the fuel injection valve I is now explained by reference to FIG. 2 to FIG. 6 .
  • a valve housing 2 of the fuel injection valve I is formed from a cylindrical valve seat member 3 having a valve seat 8 at the front end, a magnetic cylindrical body 4 coaxially and liquid-tightly joined to a rear end part of this valve seat member 3, a non-magnetic cylindrical body 6 coaxially and liquid-tightly joined to the rear end of this magnetic cylindrical body 4, a fixed core 5 coaxially and liquid-tightly joined to the rear end of this non-magnetic cylindrical body 6, and a fuel inlet tube 26 provided so as to be connected coaxially to the rear end of the fixed core 5.
  • the valve seat member 3 has a cylindrical guide hole 9 and an annular valve seat 8 communicating with the front end of this guide hole 9, and a nozzle 10 positioned on the valve seat 8 inner peripheral side, that is, the downstream side, is formed integrally with this valve seat member 3.
  • the valve seat member 3 and the nozzle 10 are formed integrally by machining the same material.
  • a recess 13 that the nozzle 10 faces is formed in a front end face of the valve seat member 3.
  • a peripheral wall of this recess 13 protects the nozzle 10 from coming into contact with other objects.
  • a plurality of fuel discharge holes 11 are bored in the nozzle 10 so as to provide communication between the interior and exterior thereof. Details of these fuel discharge holes 11 are explained later.
  • the hollow cylindrical fixed core 5 is liquid-tightly pressed into an inner peripheral face of the non-magnetic cylindrical body 6 from the rear end side, and the non-magnetic cylindrical body 6 and the fixed core 5 are thereby joined to each other coaxially.
  • a portion of a front end part of the non-magnetic cylindrical body 6 that does not have the fixed core 5 fitted into it remains, and a valve-core assembly V is housed within the valve housing 2 in a section from said portion to the valve seat member 3.
  • This valve-core assembly V is formed from a valve body 18 and a movable core 12, the valve body 18 being formed from a valve part 16 that opens and closes with respect to the valve seat 8 and a valve rod part 17 that supports the valve part 16, and the movable core 12 being linked to the valve rod part 17 and positioned coaxially opposite to the fixed core 5 while extending from the magnetic cylindrical body 4 to the non-magnetic cylindrical body 6 and being inserted thereinto.
  • the valve rod part 17 is formed so as to have a smaller diameter than that of the guide hole 9, and a radially projecting journal portion 17a is formed integrally with the outer periphery of the valve rod part 17, the journal portion 17a being slidably supported on an inner peripheral face of the guide hole 9.
  • a journal portion 17b is formed on the outer periphery of the movable core 12, the journal portion 17b being slidably supported on an inner peripheral face of the magnetic cylindrical body 4.
  • the valve-core assembly V is provided with a lengthwise hole 19 extending from a rear end face of the movable core 12 to just before the valve part 16, a plurality of first sideways holes 20a providing communication between this lengthwise hole 19 and the outer peripheral face of the movable core 12, and a plurality of second sideways holes 20b providing communication between the lengthwise hole 19 and an outer peripheral face of the valve rod part 17 between the journal portion 17a and the valve part 16.
  • an annular spring seat 24 facing the fixed core 5 side is formed partway along the lengthwise hole 19.
  • the fixed core 5 is made of a high hardness ferrite magnetic material.
  • a collar-shaped high hardness stopper element 14 surrounding the valve spring 22 is embedded in an attracting face of the movable core 12 that faces an attracting face of the fixed core 5.
  • the outer end of the stopper element 14 projects slightly from the attracting face of the movable core 12, and is usually positioned opposing the attracting face of the fixed core 5 across a gap corresponding to the valve-opening stroke of the valve body 18.
  • the fixed core 5 has a lengthwise hole 21 communicating with the lengthwise hole 19 of the movable core 12, and the fuel inlet tube 26 is provided integrally with the rear end of the fixed core 5, the interior of the fuel inlet tube 26 communicating with the lengthwise hole 21.
  • the fuel inlet tube 26 is formed from a decreased diameter portion 26a connected to the rear end of the fixed core 5 and an increased diameter portion 26b that is continuous with the decreased diameter portion 26a, and the valve spring 22 is provided in a compressed state between the spring seat 24 and a pipe-shaped retainer 23 fitted into and fixed to the lengthwise hole 21 from the decreased diameter portion 26a, the valve spring 22 urging the movable core 12 toward the side on which the valve body 18 is closed.
  • the set load of the valve spring 22 is adjusted by the depth to which the retainer 23 is fitted into the lengthwise hole 21.
  • a fuel filter 27 is fitted into the increased diameter portion 26b.
  • a coil assembly 28 is fitted around the outer periphery of the valve housing 2 so as to correspond to the fixed core 5 and the movable core 12.
  • This coil assembly 28 is formed from a bobbin 29 and a coil 30 wound therearound, the bobbin 29 being fitted onto outer peripheral faces from a rear end part of the magnetic cylindrical body 4 to the fixed core 5, the front end of a cylindrical coil housing 31 surrounding the coil assembly 28 is welded to an outer peripheral face of the magnetic cylindrical body 4, and the rear end thereof is welded to an outer peripheral face of a yoke 5a projecting in a flange shape from the outer periphery of a rear end part of the fixed core 5.
  • Part of the magnetic cylindrical body 4, the coil housing 31, the coil assembly 28, the fixed core 5, and the front half of the fuel inlet tube 26 are encapsulated by a cylindrical molded part 32 made of a synthetic resin by injection molding.
  • the interior of the coil housing 31 is also filled with the molded part 32 so as to also encapsulate the coil 30.
  • a coupler 34 is formed integrally with a middle part of the molded part 32 so as to project toward one side, and this coupler 34 retains an energization terminal 33 connected to the coil 30.
  • the annular valve seat 8 has as a basic shape a conical face whose diameter decreases in going toward the front of the fuel injection valve I, a seat part thereof for the valve part 16 is convexly curved, an annular sealing face 16a of the valve part 16 opposing the seat part is formed from part of a convex spherical surface, and an extremity face 16b of this valve part 16 is formed as a conical face having a tangent to the sealing face 16a as a generatrix.
  • both an inner end face 10a and an outer end face thereof are formed as conical faces whose diameter decreases in going toward the front of the nozzle 10, and form an overall shape that is convex toward the front of the fuel injection valve 1.
  • an annular step 15 is provided between the valve seat 8 and the inner end face 10a of the nozzle 10, the annular step 15 ensuring that there is a conical space 25 between the valve part 16 and the inner end face 10a of the nozzle 10.
  • the space 25 prevents mutual contact between the valve part 16 and the nozzle 10, gives certainty that the valve part 16 is seated on the valve seat 8, and contributes to ensuring valve sealing.
  • a plurality of fuel discharge holes 11a, 11b, and 11c bored in the nozzle 10 are now explained by reference to FIG. 3 to FIG. 6 .
  • the plurality of fuel discharge holes 11a, 11b, and 11c are arranged on the same virtual circle C having an axis A of the valve seat member 3 as the center and having a smaller diameter than that of the valve seat 8.
  • These fuel discharge holes 11a, 11b, and 11c are divided symmetrically into a first fuel discharge hole group G1 and a second fuel discharge hole group G2 with as a boundary a plane N passing through the axis A and extending in the Y direction (the direction orthogonal to the arrangement direction of the first and second intake ports P1 and P2).
  • a gap D2 between adjacent fuel discharge holes 11a, 11b, and 11c of each of the fuel discharge hole groups G1 and G2 is set so as to be smaller than a gap D1 between the two fuel discharge hole groups G1 and G2.
  • the number of fuel discharge holes forming each of the fuel discharge hole groups G1 and G2 is three, that is, 11a to 11c.
  • the fuel discharge holes 11a, 11b, and 11c are arranged so that their center lines La, Lb, and Lc are substantially parallel to the axis A of the valve seat member 3.
  • the angle formed between the center line La, Lb, Lc of each of the fuel discharge holes 11a, 11b, and 11c and the conical concave inner end face 10a of the nozzle 10 is an obtuse angle ⁇ on the side closer to the outer periphery of the nozzle 10 with respect to the center line La, Lb, and Lc, and an acute angle ⁇ on the side closer to the center of the nozzle 10 with respect to the center line La, Lb, Lc.
  • the two fuel discharge holes 11a and 11c on opposite outer positions are arranged so that the two center lines La and Lc intersect each other at an intersection point Q in front of the nozzle 10 and toward one side, closer to the center of the nozzle 10, of an extension of the center line Lb of the fuel discharge hole 11b at the middle position or its vicinity of the respective fuel discharge hole group G1, G2.
  • valve-core assembly V In a state in which the coil 30 is de-energized, the valve-core assembly V is pushed forward by means of the urging force of the valve spring 22 to thus seat the valve body 18 on the valve seat 8.
  • fuel that has been fed under pressure from a fuel pump, which is not illustrated, to the fuel inlet tube 26 passes through the interior of the pipe-shaped retainer 23 and the lengthwise hole 19 and first and second sideways holes 20a and 20b of the valve-core assembly V, is held in readiness within the valve seat member 3, and is used for lubrication of a section around the journal portions 17a and 17b of the valve-core assembly V.
  • the main flow includes an inward flow S1, which flows directly from the valve seat 8 to the fuel discharge holes 11a, 11b, and 11c, and an outward flow S2, which passes between adjacent fuel discharge holes 11a, 11b, and 11c, comes together in a central part of the inner end face 10a, then advances radially outwardly, and flows into the fuel discharge holes 11a,11b, and 11c.
  • the angle formed between the center lines La, Lb, and Lc of the fuel discharge holes 11a, 11b, and 11c and the conical concave inner end face 10a of the nozzle 10 is set at the obtuse angle ⁇ on the side closer to the outer periphery of the nozzle 10 with respect to the center lines La, Lb, and Lc
  • the angle formed between the direction of the inward flow S1 and one inside face, on the side closer to the outer periphery of the nozzle 10, of the fuel discharge holes 11a, 11b, and 11 c is also an obtuse angle, and the inward flow S1 is straightened while being guided by said one inside face and flows outside the fuel discharge holes 11a, 11b, and 11c, the energy loss being thus very small.
  • the angle between the center lines La, Lb, and Lc of the fuel discharge holes 11a, 11b, and 11c and the conical concave inner end face 10a of the nozzle 10 is set at the acute angle ⁇ on the side closer to the center of the nozzle 10a with respect to the center lines La, Lb, and Lc, the angle between the direction of the outward flow S2 and the other inside face, on the side closer to the center of the nozzle 10, of the fuel discharge holes 11a, 11b, and 11c is also an acute angle, and even though it flows into the fuel discharge holes 11a, 11b, and 11c the outward flow S2 is combined with the inward flow S1 while separating from said other inside face.
  • fuel injected from the fuel discharge holes 11a, 11b, and 11c produces fuel spray forms fa, fb, and fc as fuel films having an arc-shaped cross section with a convex face facing toward the outer periphery of the nozzle 10 as shown in FIG. 4 and FIG. 6 . Therefore, since the fuel spray forms fa, fb, and fc are produced as fuel films having an arc-shaped cross section, the outline is clear and wasteful scattering does not occur and, moreover, since the loss of fuel injection energy is small overall, the penetration properties of the fuel spray forms fa, fb, and fc can be improved.
  • the fuel films having an arc-shaped cross section producing the fuel spray forms fa, fb, and fc increase in diameter and greatly decrease in film thickness in going toward the intake valve Ei of the engine E, and finally exhibit a good atomization state as a result of high speed contact with air, and it is therefore possible to improve the atomization at the extremities of the fuel spray forms fa, fb, and fc close to the intake valve Ei.
  • first and second fuel spray forms fa, fb, and fc as arc-shaped cross section fuel films injected and produced from the three fuel discharge holes 11a, 11b, and 11c as described above form two independent, that is, first and second, fuel spray-form beams F1 and F2, and these first and second fuel spray-form beams F1 and F2 are supplied to the first and second intake ports P1 and P2 respectively.
  • the fuel spray forms fa and fc injected and produced from the two fuel discharge holes 11a and 11c on opposite outer positions are inclined toward the fuel spray form fb injected and produced from the fuel discharge hole 11b at the middle position, the fuel spray-form beams F1 and F2 having clear outlines can be produced, and this can enhance further effectively the penetration properties of the fuel spray-form beams F1 and F2.
  • the fuel spray-form beams F1 and F2 having thus enhanced penetration properties are resistant to becoming attached to an inner wall of the first and second intake ports P1 and P2, the engine combustion efficiency can be improved, and a contribution
  • each of the fuel discharge hole groups G1 and G2 since the center lines La, Lb, and Lc of the fuel discharge holes 11a, 11b, and 11c are substantially parallel to the axis A of the valve seat member 3, machining of each of the fuel discharge holes 11a, 11b, and 11c by means of piercing or a laser can be carried out easily without being affected by surrounding objects, such as a peripheral wall of the valve seat member 3.
  • valve seat member 3 and the nozzle 10 are integrated using the same material, not only can a step of joining to the valve seat member 3 by welding, etc. be omitted and the production step and the structure be simplified, but it is also possible to prevent the valve seat 8 from being distorted by a joining step and improve the precision of the valve seat 8 and, consequently, the valve sealing. Furthermore, it is possible to easily carry out machining of the fuel discharge holes 11a,11b, and 11c at the correct positions with respect to the valve seat 8, and dimensional control can also be carried out easily.
  • FIG. 7 shows a modified example of the fuel injection valve I.
  • an extremity face 16b of a valve part 16 is formed from a spherical face having the same diameter R1 as that of a valve seat 8, and an inner end face 10a of a nozzle 10 opposing the extremity face 16b is formed from a spherical face having a diameter R2 that is larger than the diameter R1.
  • the arrangement thereof is the same as the preceding embodiment; portions in FIG. 7 corresponding to the preceding embodiment are denoted by the same reference numerals and symbols, and duplication of the explanation is therefore omitted.
  • the same operational effects as those of the preceding embodiment can also be exhibited.
  • the present invention is not limited to the above-mentioned embodiment and may be modified in a variety of ways as long as the modifications do not depart from the scope thereof.
  • the number of the plurality of fuel discharge holes 11a, 11b, and 11c forming each of the fuel discharge hole groups G1 and G2 may be any of three or greater for the invention.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
EP10761560.1A 2009-03-30 2010-03-15 Fuel injection valve Not-in-force EP2416000B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009083535A JP5312148B2 (ja) 2009-03-30 2009-03-30 燃料噴射弁
PCT/JP2010/054325 WO2010116859A1 (ja) 2009-03-30 2010-03-15 燃料噴射弁

Publications (3)

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EP2416000A1 EP2416000A1 (en) 2012-02-08
EP2416000A4 EP2416000A4 (en) 2014-04-16
EP2416000B1 true EP2416000B1 (en) 2016-01-06

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EP10761560.1A Not-in-force EP2416000B1 (en) 2009-03-30 2010-03-15 Fuel injection valve

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US (1) US20120006300A1 (ja)
EP (1) EP2416000B1 (ja)
JP (1) JP5312148B2 (ja)
CN (1) CN102369350B (ja)
WO (1) WO2010116859A1 (ja)

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US9663894B2 (en) * 2005-11-10 2017-05-30 Lg Electronics Inc. Steam generator and laundry dryer having the same and controlling method thereof
KR101067316B1 (ko) * 2009-06-22 2011-09-23 주식회사 아이노바 돔 형상의 선형 압전 모터
DE102010032640A1 (de) * 2010-07-29 2012-02-02 Continental Automotive Gmbh Düsenkörper, Düsenbaugruppe und Kraftstoffinjektor
JP5295315B2 (ja) * 2011-06-22 2013-09-18 三菱電機株式会社 燃料噴射弁
CN107178449B (zh) * 2016-03-10 2019-11-08 株式会社京浜 缸内喷射用电磁式燃料喷射阀
JP6190917B1 (ja) * 2016-05-09 2017-08-30 三菱電機株式会社 燃料噴射弁
JP2017210890A (ja) * 2016-05-24 2017-11-30 日立オートモティブシステムズ株式会社 流量調整弁
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WO2010116859A1 (ja) 2010-10-14
EP2416000A1 (en) 2012-02-08
JP5312148B2 (ja) 2013-10-09
CN102369350A (zh) 2012-03-07
JP2010236390A (ja) 2010-10-21
US20120006300A1 (en) 2012-01-12
EP2416000A4 (en) 2014-04-16

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